CN108691770A - Helical-lobe compressor - Google Patents
Helical-lobe compressor Download PDFInfo
- Publication number
- CN108691770A CN108691770A CN201810284820.6A CN201810284820A CN108691770A CN 108691770 A CN108691770 A CN 108691770A CN 201810284820 A CN201810284820 A CN 201810284820A CN 108691770 A CN108691770 A CN 108691770A
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- mentioned
- motor
- helical
- downstream side
- maintaining part
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
Abstract
The present invention provides helical-lobe compressor, can prevent the temperature rise of the part of winding and improve performance and reliability, expands operating range, have:Motor (4);By the male rotor (11) and female rotor (12) of motor drive;And it stores motor (4) and male rotor (11) and female rotor (12) and has the maintaining part (1a, 1b) of the periphery of holding motor (4) and be formed with the shell (1,2) for the suction inlet (6) that the gas after motor (4) is oriented to male rotor (11) and female rotor (12).At the circumferential both ends of maintaining part (1b), the gas passage (4b) of gas flowing is formed by the outside wall surface (20c) of motor (4) and the internal face (1d) of motor shell (1), there is maintaining part (1b) end of downstream side (1b2) positioned at the downstream side of gas flow, the width that end of downstream side (1b2) is configured to circumferential to be reduced with towards downstream side.
Description
Technical field
The present invention relates to helical-lobe compressors.
Background technology
Hermetic type helical-lobe compressor is by screw rotor, the low pressure side bearing of supporting screw rotor and high pressure side bearing, driving
The motor of screw rotor and the shell for storing these components are constituted.Although motor can be configured at low-pressure side and high pressure
The either side of side, if but be configured at low-pressure side, since the refrigerant gas of low temperature, low pressure can be utilized to cool down the electronic of fever
Machine, therefore the case where being configured at low-pressure side, is more.
The motor for being configured at low-pressure side is led to by the gas constituted between shell inner peripheral surface and motor stator peripheral surface
Road area of section (hereinafter referred to as " motor periphery passage sections area ".) and in motor stator inner peripheral surface and motor rotor
The gas passage area of section (hereinafter referred to as " free cross-section area " constituted between peripheral surface.) constitute, in order to utilize low-pressure side
Refrigerant gas effectively cool down motor, need the ratio of motor periphery passage sections area and free cross-section area
It is optimized, but the gas passage shape around known actually motor winding end also plays in terms of cooling motor
Important role, the method as the cooling efficiency for improving motor, it is known to which that is, method that following technology is recorded, adjusts
Motor periphery passage sections area come increase the gas flow rate of refrigerant gas technology (referring to patent document 1 and patent text
It offers 2) or gas collisions component is made to be arranged and make gas collisions behind motor winding end, thus from motor
Coil end technology (with reference to patent document 3) etc. from top to lower flow refrigerant gas.
Existing technical literature
Patent document
Patent document 1:Japanese Unexamined Patent Application 58-032990 bulletins
Patent document 2:Japanese Unexamined Patent Publication 01-237389 bulletins
Patent document 3:Japanese Unexamined Patent Publication 2013-167211 bulletins
Invention content
Problems to be solved by the invention
In order to merely with the effectively cooling motor of sucking refrigerant gas, preferably include heat-resisting temperature to as component parts
Spend low resin material motor winding portion be equably in direct contact low temperature, low pressure refrigerant gas, but exist ask as follows
Topic:If gas flow rate is made to increase to necessity or more, due to the increase of the pressure loss of flowing, the specific volume of refrigerant gas increases
And refrigerating capacity declines.
It is therefore preferable that in use scope, by electromotor winding temperature become heat resisting temperature it is below in a manner of adjust refrigeration
The flowing of agent gas, and the required refrigerant gas of cooling for contacting motor, hereby it is achieved that electromotor winding temperature and pressure
Power loss and deposit.
In technology recorded in patent document 1 and patent document 2, most of refrigerant gas is gas passage less to resistance
The big place flowing of area of section, accordingly, it is difficult to refrigerant gas equably be flowed to the winding of motor, in motor winding
Foundation portion of portion generate refrigerant gas delay, become winding part temperature rise the main reason for.
In technology recorded in patent document 3, it is being located at downside compared to motor reel center to the suction inlet of screw rotor,
And it is more upper than motor reel center have motor periphery access in the case of, in the motor winding of screw rotor side
Portion carries out temperature rise than the winding portion of motor reel center on the lower.
This is because there is no periphery access than the downside of motor reel center on the lower or adjusting the flow direction of refrigerant gas
Guide part and be equipped with suction inlet, therefore, from periphery access flow out and along motor winding portion peripheral surface flow refrigerant gas
The major part of body will not reach winding peripheral surface lower end, and be sucked into suction inlet.Therefore, refrigerant gas is in winding peripheral surface
Lower end is detained, and winding temperature locally rises, and therefore, it is necessary to limit operating range.
In addition, logical motor periphery is arranged on the lower than motor reel center in order to cool down winding peripheral surface lower end
It is (electronic to suction inlet direction in the refrigerant gas of the gas passage flowing than motor reel center on the lower in the case of road
Arbor to) flowing, therefore contact with motor winding and to carry out shorter at a distance from heat exchange, it is whole cannot effectively cool down winding.
In addition, in the case where reducing the underside gas area of passage for Temperature Distribution adjustment, the pressure loss increases and performance declines.
Therefore, the object of the present invention is to provide a kind of helical-lobe compressors, can prevent the temperature rise of the part of winding
And it improves performance and reliability, expand operating range.
Solution for solving the problem
In order to solve the above problems, one embodiment of the present invention is a kind of helical-lobe compressor, is had:Motor;Screw rod
Rotor, by above-mentioned motor drive;Shell stores above-mentioned motor and screw rotor, has and keeps above-mentioned motor
The maintaining part of periphery, and it is formed with the suction inlet that the gas after motor is oriented to above-mentioned screw rotor, in above-mentioned holding
The circumferential both ends in portion, are formed the gas passage of gas flowing by the outside wall surface of above-mentioned motor and the internal face of above-mentioned shell,
There is above-mentioned maintaining part the end of downstream side positioned at the downstream side of gas flow, above-mentioned end of downstream side to be configured to, circumferential width
Degree is reduced with towards downstream side.
Invention effect
In accordance with the invention it is possible to provide the temperature rise for the part that can prevent winding and improve performance and reliability, expansion
The helical-lobe compressor of big operating range.
Description of the drawings
Fig. 1 is the integrally-built longitudinal section view for the helical-lobe compressor for indicating embodiment of the present invention.
Fig. 2 is the A-A regarding sectional views of Fig. 1.
Fig. 3 is not form hill condition, along the line B-B cut-out motor shell of Fig. 2 and the shape of main casing in maintaining part
The stereogram of state is the detailed figure of the flowing of the maintaining part and refrigerant gas before suction inlet.
Fig. 4 is not form hill condition, along the line B-B cut-out motor shell of Fig. 2 and the shape of main casing in maintaining part
The stereogram of state is the detailed figure of the flowing of the maintaining part and refrigerant gas before suction inlet.
Fig. 5 is to form slope in maintaining part and guide part situation, B- along Fig. 2 is arranged in the internal face of motor shell
B lines cut off the stereogram of the state of motor shell and main casing, are the flowing of the maintaining part 1b and refrigerant gas before suction inlet
Detailed figure.
Fig. 6 is from the C-C of Fig. 5 to the figure from apparent direction.
Fig. 7 is to constitute guide part situation by multiple guide parts, cut off motor shell and main casing along the line B-B of Fig. 2
State stereogram, be the detailed figure of the flowing of the maintaining part and refrigerant gas before suction inlet.
Fig. 8 is the enlarged view of the main part of the shape on the slope of variation.
Symbol description
1-motor shell, 1a, 1b-maintaining part, 1b2-end of downstream side, 1b3-end face, 1d-internal face, 2-is main
Shell, 4-drive motors, the gas passage 4a, 4b-, 6-suction inlets, 11-male rotors, 12-female rotors, 20-is fixed
Son, the first winding portion of 20a-, the second winding portion of 20b-, 20c-outside wall surface, 20d-end face, 21-rotors, 30-slopes,
30a-arc sections, 30b-tapered portion, 31-guide parts, 31a-end face, 32-spaces, 100-sides, 101-gas passages
Side, 110-helical-lobe compressors.
Specific implementation mode
Hereinafter, using the helical-lobe compressor 110 of description of the drawings embodiment of the present invention.In addition, in each figure, it is labelled with identical
The part of symbol indicates same or equivalent part.
Hereinafter, illustrating the overall structure of the helical-lobe compressor 110 of embodiment of the present invention.
Fig. 1 is the integrally-built longitudinal section view for the helical-lobe compressor 110 for indicating embodiment of the present invention.
The helical-lobe compressor 110 of present embodiment is the double-screw compressor of hermetic type.
In helical-lobe compressor 110, motor shell 1, main casing 2 and ejection shell 3 are interconnected to sealing relationship, constitute shell
Body.In addition, shell is formed by casting.
It is accommodated in motor shell 1 for driving the drive motor 4 of compression mechanical part (hereinafter simply referred to as electronic
Machine 4).The motor 4 has the stator 20 being fixed in motor shell 1 and the inside for being rotatably freely set to the stator 20
Rotor 21.
Protrude the first winding portion 20a (coil end) in winding to the upstream side from stator 20.Downstream from stator 20
Side protrudes the second winding portion 20b (coil end) in winding.In the present embodiment, the diameter and second of the first winding portion 20a
Diameter of the diameter of winding portion 20b respectively than stator 20 is small.First winding portion 20a and the second winding portion 20b are respectively provided with conduct
The neck of the part to connect with stator 20.Other parts of the diameter of neck than the first winding portion 20a and the second winding portion 20b
Diameter is small.
It is formed with suction inlet 18 in the end of motor shell 1.The filter 19 of trapping foreign matter is installed in suction inlet 18.It should
Filter 19 is fixed flange 65 and motor shell 1 is clamped and fixes.It is being made in addition, being connected in fixed flange 65 for sucking
The sucking of the refrigerant recycled in SAPMAC method is piped.
It is formed with cylindrical hole 5 in main casing 2 and the suction inlet 6 for importing refrigerant gas to the cylindrical hole 5.Separately
Outside, the suction side axle portion of male rotor 11 is supported by the roller bearing 7 (low pressure side bearing) for being disposed in motor shell 1.Male rotor 11
Ejection side axle portion by be disposed in spray shell 3 roller bearing 8 and ball bearing 9 (high pressure side bearing) support.In addition, turning with sun
The suction side axle portion for the female rotor 12 (with reference to Fig. 3) that son 11 parallelly configures (is not schemed by the roller bearing for being disposed in motor shell 1
Show) bearing.The axis of female rotor 12 relative to male rotor 11 axle position in the vertical direction in the section of the figure.The spray of female rotor 12
Go out roller bearing and ball bearing bearing (not shown) that side axle portion sprays shell 3 by being disposed in.12 phase of male rotor 11 and female rotor
Mutually engagement, and supported and stored in a manner of it can rotate by main casing 2.By male rotor 11 and female rotor 12, composition is mutually nibbled
Negative and positive a pair of screw rotor of conjunction.Compression mechanical part is constituted by the screw rotor and the cylindrical hole 5 etc. for being formed in main casing 2.
The upstream side of refrigerant gas is known as low-pressure side relative to screw rotor, downstream side is known as high-pressure side.
The axis of male rotor 11 is directly linked to the rotor 21 of motor 4 in low-pressure side.In addition, in the side of main casing 2 one
Body is formed with oil eliminator 13.Compressed refrigerant gas and oil are detached into oil eliminator 12 in compression mechanical part.
Oil after separation lodges in the store oil portion 14 formed in 13 lower part of oil eliminator.Roller bearing 8 and ball are stored in spraying shell 3
Bearing 9.In addition, being formed with the ejection access (not shown) for the refrigerant gas being connected to oil eliminator 13 in spraying shell 3.
The ejection shell 3 is bolted in main casing 2.In addition, being formed with storage roller bearing 8 and ball bearing 9 in shell 3 spraying
Bearing chamber 16.In addition, the shield 17 for closing bearing chamber 16 is installed on the terminal part for spraying shell 3.
The capacity being made of guiding valve 26, bar 27, hydraulic piston 28 and helical spring 29 etc. is equipped in helical-lobe compressor 110
Control mechanism portion.Guiding valve 26 is received in the recess portion 2a being formed in main casing 2 in a manner of moving back and forth freely in the axial direction
It receives.The position of the guiding valve 26 is set to move, to suck one of male rotor 11 and the refrigerant gas of the engaging section of female rotor 12
Divide and bypassed to suction inlet side, the capacity of helical-lobe compressor 110 can be controlled.
Bar 27, hydraulic piston 28 and helical spring 29, which are accommodated in, to be sprayed in shell 3.Wherein, hydraulic piston 28 and spiral bullet
Spring 29, which is accommodated in, to be sprayed in the cylinder chamber Q formed in shell 3.Helical spring 29 is supported in cylinder chamber Q and compares hydraulic piston 28
It is configured at 26 side of guiding valve, to always give the power pushed to the opposite direction of guiding valve 26 to hydraulic piston 28.
Hydraulic piston 28 is accommodated in a manner of it can slide in the axial direction in cylinder chamber Q.By into cylinder chamber Q plus, oil extraction
Oil mass is adjusted, to make hydraulic piston 28 move.The action of the hydraulic piston 28 is transferred to guiding valve 26 via bar 27, to sliding
The position of valve 26 is moved in the axial direction, can operate helical-lobe compressor 110 with scheduled capacity.
In addition, in Fig. 1, omit for into cylinder chamber Q plus, oil extraction adjust the hydraulic system and opening and closing hydraulic system of oil mass
Solenoid valve etc. diagram.
Then, illustrate the flowing of the refrigerant gas in helical-lobe compressor 110.
The flowing of the refrigerant gas of the low temperature, low pressure that are sucked in motor shell 1 from suction inlet 18 is caught with filter 19
It is divided into after collection foreign matter:The upside gas passage 4a being set between motor 4 and motor shell 1;Cross side gas passage 4b
(with reference to Fig. 2);And the flow path of the gap 4c between the stator 20 and rotor 21 of motor 4.
Change after the lower section that filter 19 flows to motor 4 and flows to and refrigerant gas cooling first upward
Winding portion 20a, by after the upside gas passage 4a that is set between motor 4 and motor shell 1, with next to second around
The collision of wall that group portion 20b is arranged below, cooling second winding portion 20b, and from the overhead stream of the second winding portion 20b to lower part,
Then, it flow to suction inlet 6.In addition, flowing to a part cooling first for the refrigerant gas of the lower section of motor 4 from filter 19
Winding portion 20a, by after the cross side gas passage 4b that is set between motor 4 and motor shell 1, cooling second winding
Then the lower part of portion 20b flow to suction inlet 6.
In addition, refrigerant gas is by gap 4c, on the inside of cooling first winding portion 20a and the second winding portion 20b.
Fig. 2 is the A-A regarding sectional views of Fig. 1.
The figure shows upside gas passage 4a and cross side gas passage 4b and gap 4c and motor maintaining parts 1a, 1b
Position relationship.As shown in the drawing, upside gas passage 4a and cross side gas passage 4b can also be multiple accesses.Here, will
The periphery of stator 20 is known as outside wall surface 20c.Maintaining part 1a, 1b stored and keep motor 4 is equipped in motor shell 1.In addition,
Upside gas is formed using the outside wall surface 20c of the recess portion 1c and stator 20 that are formed by the internal face 1d equipped with maintaining part 1a, 1b to lead to
Road 4a and cross side gas passage 4b.In addition, maintaining part 1b is configured to keep the downside of stator 20, the as a result, downside of stator 20
It is blocked, does not form gas passage.Moreover, the circumferential both ends in maintaining part 1b are formed with cross side gas passage 4b.
In the case where suction inlet 6 is located at downside compared to the axis center of motor 4, the axis center compared to motor 4 is located at
The temperature of the winding of upside is easy to rise.Therefore, multiple respective at least part of upside gas passage 4a are set to upside,
It is easy the entirety of cooling motor 4.In addition, suction inlet 6 is set to downside relative to the axis center of motor 4 indicates male rotor 11
Axis center with female rotor 12 relative to motor 4 sucks refrigerant gas from downside.
Then, illustrate the flowing of the oil in helical-lobe compressor 110 referring to Fig.1.
Male rotor 11 and the mesh tooth face and main casing 2 of female rotor 12 form discharge chambe (compression work room).By motor 4
Refrigerant gas after cooling is inhaled into discharge chambe from the suction inlet 6 for being formed in main casing 2.Then, with direct with motor 4
The rotation of the male rotor 11 of connection, refrigerant gas are enclosed within discharge chambe, are gradually compressed because of the diminution of discharge chambe, become high
The refrigerant gas of temperature, high pressure, and sprayed into oil eliminator 13.
About the radial load in the compression counter-force for acting on male rotor 11 and female rotor in above-mentioned compression, by Roller Shaft
7,8 bearings are held, are supported by ball bearing 9 about thrust load.
The supply of the oil of the lubrication of these roller bearings 7,8 and ball bearing 9 is illustrated.
First, as the oil in the store oil portion 14 of the on high-tension side oil eliminator 12 of main casing 2 because of the differential pressure with low-pressure side, profit
Sliding and cooling low pressure side bearing (inhalation side bearings;Roller bearing 7), and be discharged to 6 side of suction inlet.In addition, the oil in store oil portion 14
Lubrication and cooling high pressure side bearing (spray side bearing;Roller bearing 8, ball bearing 9), and just completed to 6 side of suction inlet or sucking
The discharges such as discharge chambe later.
The oil being discharged after each bearing lubrication flows together with compression refrigerant gas while lubricating discharge chambe, with pressure
Contraction refrigerant gas sprays together, and is flowed into oil eliminator 13.Using the oil eliminator 13, oil lodges in again to be set to
The store oil portion 14 of 12 lower part of oil eliminator, compression refrigerant gas are conveyed from ejiction opening 22 to refrigeration cycle.
Then, flowing and the effect of slope 30 and guide part 31 of the refrigerant gas before suction inlet 6 are explained in detail.
Fig. 3 is not form 30 situation of slope, along the line B-B cut-out motor shell 1 and main casing of Fig. 2 in maintaining part 1b
The stereogram of 2 state is the detailed figure of the flowing of the maintaining part 1b and refrigerant gas before suction inlet 6.
In the figure, the arrow A in figure indicates the flow direction of refrigerant gas.Hereinafter, will flow along the directions arrow A
Refrigerant gas is known as refrigerant gas A.Since the shape of the end of downstream side 1b2 of maintaining part 1b is that circumferential width does not become
Angle (edge) 1b1 shapes of change, thus the refrigerant gas flowed in the 4b of gas passage from gas passage 4b along the directions arrow A
Outflow, and be directly inhaled into 6 direction of suction inlet.As a result, in the flow stagnation of the downstream side refrigerant gas of maintaining part 1b,
It is not sufficiently cooled near the lower end of two winding portion 20b, temperature rise.Especially under the neck of the second winding portion 20b
Portion's temperature rise.
Fig. 4 is to be formed with 30 situation of slope, along the line B-B cut-out motor shell 1 and main casing of Fig. 2 in maintaining part 1b
The stereogram of 2 state is the detailed figure of the flowing of the maintaining part 1b and refrigerant gas before suction inlet 6.
In Fig. 4, maintaining part 1b has the end of downstream side 1b2 in the downstream side of the flow direction positioned at refrigerant gas A, in downstream
The circumferential both ends of the end face 1b3 of side end 1b2 are formed with relative to the inclined slope in orthogonal with motor reel face 30.Maintaining part
The end of downstream side 1b2 of 1b is configured to circumferential width because of slope 30 to be reduced with towards downstream side.
A part of the refrigerant gas A flowed in the 4b of gas passage as a result, because Coanda effect along slope 30 flow,
Therefore, flow direction disorder will not be made just can a part for the flowing of refrigerant gas A swimmingly to be carried out branch.System after branch
Refrigerant gas B flows into the downstream side of maintaining part 1b, and therefore, the energy of flow gets at the lower section up to the second winding portion 20b, and can cool down
The lower end of the peripheral surface of second winding portion 20b.Therefore, it is possible to the temperature rise for providing the part that can prevent winding and raising property
Energy and reliability, the helical-lobe compressor 110 for expanding operating range.
Then, to also setting up guide part 31 other than in the case where maintaining part 1b forms slope 30 the case where, is said
It is bright.
Fig. 5 be maintaining part 1b formed slope 30 and the internal face 1d of motor shell 1 be provided with 31 situation of guide part,
The stereogram that the state of motor shell 1 and main casing 2 is cut off along the line B-B of Fig. 2 is maintaining part 1b and system before suction inlet 6
The detailed figure of the flowing of refrigerant gas.
As shown in figure 5, the downstream side of the internal face 1d and maintaining part 1b of motor shell 1 position with end of downstream side
Mode opposed 1b2 is provided with from internal face 1d guide parts 31 outstanding.The height away from internal face 1d of guide part 31 is set as
The outside wall surface 20c and the distance between the internal face 1d of motor shell 1 of motor 4 than forming gas passage 4b are high.In addition, leading
To part 31 along motor 4 axis it is circumferentially disposed, and be set on the internal face 1d of motor shell 1 with the second winding portion
Position opposed 20b.
In this way, will not make to be in direct contact with guide part 31 from the flowing that slope 30 flows out, slope 30 can will be utilized
Make flow direction change into circumferential refrigerant gas to flow along guide part 31, therefore the increase of the pressure loss can be inhibited, and flows
Guide part 31 will not be crossed and flowed out to 6 side of suction inlet, refrigerant gas flow can be made to the lower end of the second winding portion 20b
Portion.Therefore, it is possible to provide the temperature rise for the part for preventing winding and improve performance and reliability, the screw rod for expanding operating range
Compressor 110.
Fig. 6 is from the C-C of Fig. 5 to the figure from apparent direction.
In Fig. 6, it is equipped with slope 30 at the both ends of the outlet side of maintaining part 1b, refrigerant gas B is mutually relatively flowed into, because
This, refrigerant gas B can collide upward direction flowing, and be in direct contact to the lower surface of the second winding portion 20b and neck
Gas flows, and can increase cooling effect.
In addition, the side 100 of guide part 31 can also be set to the inside of the circumferential side 101 of gas passage 4b.It is logical
It crosses and is configured so that, flow to since the refrigerant gas A flowed in the 4b of gas passage will not be contacted with guide part 31 and swimmingly
Suction inlet side, therefore, the pressure loss of flowing will not increase, being capable of rejection decline.
Then, the case where illustrating to be made of guide part 31 multiple guide parts 31.
Fig. 7 be by guide part 31 by multiple guide parts 31 constitute situation, along Fig. 2 line B-B cut off motor shell 1 and
The stereogram of the state of main casing 2 is the detailed figure of the flowing of the maintaining part 1b and refrigerant gas before suction inlet 6.
In Fig. 7, guide part 31 is made of two guide parts 31 circumferentially arranged, is formed between guide part 31 free
Between 32.Thereby, it is possible to the part that the refrigerant gas B in the downstream side of maintaining part 1b is flowed into from slope 30 is swimmingly flowed to suction
Entrance 6 can inhibit the resistance of flowing.In addition, the circumferential length of adjustment guide part 31, by the position in space 32 relative to the
The heating part of two winding portion 20b is set near its radial direction, and the refrigerant gas B to be flowed into from the both sides of maintaining part 1b is in sky
Between 32 position near collide, can directly flow refrigerant gas to the surface of heating part and jaw portion, cooling effect is more
Greatly.
Here, for slope 30, (direction and the formation of slope 30 of refrigerant gas A are reduced by deepening inclined surface
Angle), the flow rate of refrigerant gas into winding lower part can be increased, cooling effect can be further increased.That is, being capable of basis
The depth on the temperature adjustment slope 30 of heating part, it is ensured that the flow of cooling required refrigerant gas.
The end face 20d in downstream sides of the end face 31a of the upstream side of guide part 31 compared to the second winding portion 20b is located at upstream
Side.Thereby, it is possible to the second winding portion 20b flowing underneath refrigerant gas.
The radial height of guide part 31 can in the range of can ensure the insulation distance with the second winding portion 20b according to
The flow direction of refrigerant gas changes.The radial height of guide part 31 if it is the height of gas passage 4b more than, then freeze
Agent gas will not cross guide part 31 and be flowed out to suction inlet 6, it can be ensured that flow to the flow below the second winding portion 20b.Cause
This, the radial height of guide part 31 be preferably able to ensure the insulation with the second winding portion 20b and for the height of gas passage 4b with
On.
(a), (b) of Fig. 8 is the enlarged view of the main part of the shape on the slope 30 of variation.
Such as (a) of Fig. 8, for slope 30, it is only arc sections (arc surface) 30a to make the inclined surface on slope 30.In addition, figure
In 8 (b), it is the shape for being combined with arc sections (arc surface) 30a and tapered portion (plane) 30b to make the inclined surface on slope 30.Appoint
In one variation, the shape of the end of downstream side 1b2 of maintaining part 1b is configured to circumferential width and is reduced with towards downstream side.
In addition, as long as the shape of the end of downstream side 1b2 of maintaining part 1b is configured to circumferential width with being reduced towards downstream side, then appoint
Shape of anticipating can.
As described above, according to the embodiment of the present invention, the temperature rise that can prevent the part of winding, keeps winding whole
The temperature row of body homogenizes.Moreover, the increase of the pressure loss can be inhibited, therefore the performance of helical-lobe compressor 110 can be improved
And reliability, and expand operating range.
In above-mentioned embodiment, suction inlet 6 and slope 30 and guide part 31 are relative to axis and the moon comprising male rotor 11
The imaginary plane of the axis of rotor 12 is set to same side, but such as regardless of the position relationship of slope 30, guide part 31 and suction inlet 6
What, in the case of composition in circumferential wider width of the circumferential width of specific maintaining part 1b than other maintaining part 1a,
Since flowing is easy to stagnate in side downstream, to specific maintaining part 1b settings slope 30, the guide part 31.As a result,
Can inhibit the stagnation in the downstream side of maintaining part 1b, and prevent winding office temperature rise.
Embodiments of the present invention are not limited to the double-screw compressor of hermetic type, can also be suitable for the double of semi-hermetic type
Helical-lobe compressor.Alternatively, it is also possible to be single screw compressor etc., other helical-lobe compressors, if it is the stream in refrigerant gas
Screw rotor is arranged in the downstream of motor in Lu Zhong, and refrigerant gas sucks spiral shell relative to the axis of motor from specific direction
Bar rotor can then apply the present invention.This helical-lobe compressor can be used in air-conditioning, cold unit, refrigeration machine etc..
In addition, the above embodiments are the embodiments for for easy understanding illustrating the present invention and explaining in detail, may not limit
Due to the embodiment for the entire infrastructure for having explanation.In addition, can other realities be replaced as a part for the structure of certain embodiment
The structure of example is applied, in addition, can also add the structure of other embodiments to the structure of certain embodiment.In addition, can be to each implementation
A part for the structure of example carries out the addition of other structures, eliminates, replaces.
Claims (7)
1. a kind of helical-lobe compressor, which is characterized in that
Have:
Motor;
Screw rotor, by above-mentioned motor drive;And
Shell stores above-mentioned motor and screw rotor, has the maintaining part for the periphery for keeping above-mentioned motor, and be formed with
Gas after motor is oriented to the suction inlet of above-mentioned screw rotor,
At the circumferential both ends of above-mentioned maintaining part, gas stream is formed by the outside wall surface of above-mentioned motor and the internal face of above-mentioned shell
Dynamic gas passage,
There is above-mentioned maintaining part the end of downstream side positioned at the downstream side of gas flow, above-mentioned end of downstream side to be configured to, circumferential
Width reduced with towards downstream side.
2. helical-lobe compressor according to claim 1, which is characterized in that
The downstream side of the internal face and above-mentioned maintaining part of above-mentioned shell position in a manner of opposed with above-mentioned end of downstream side
Equipped with from above-mentioned internal face guide part outstanding.
3. helical-lobe compressor according to claim 1, which is characterized in that
Above-mentioned guide part is made of the multiple guide parts circumferentially arranged, and space is formed between adjacent guide part.
4. helical-lobe compressor according to claim 2 or 3, which is characterized in that
The circumferential two sides of above-mentioned guide part are located inside compared to the circumferential two sides of above-mentioned maintaining part.
5. the helical-lobe compressor according to any one of claim 2~4, which is characterized in that
The height away from above-mentioned internal face of above-mentioned guide part is set as the above-mentioned of the above-mentioned motor than forming above-mentioned gas access
The distance between outside wall surface and the above-mentioned internal face of above-mentioned shell are high.
6. the helical-lobe compressor according to any one of claim 2~5, which is characterized in that
Above-mentioned motor has:
Stator forms above-mentioned outside wall surface;And
Coil end is downstream protruded from said stator,
The end face of the upstream side of above-mentioned guide part is located at upstream side compared to the end face in the downstream side of above-mentioned coil end.
7. according to helical-lobe compressor according to any one of claims 1 to 6, which is characterized in that
Above-mentioned maintaining part is configured to, and the circumferential width of other maintaining parts of the circumferential width than keeping above-mentioned motor is wide.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017077538A JP7075721B2 (en) | 2017-04-10 | 2017-04-10 | Screw compressor |
| JP2017-077538 | 2017-04-10 |
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| Publication Number | Publication Date |
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| CN108691770A true CN108691770A (en) | 2018-10-23 |
| CN108691770B CN108691770B (en) | 2019-12-10 |
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| Country | Link |
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| JP (1) | JP7075721B2 (en) |
| CN (1) | CN108691770B (en) |
| DE (1) | DE102018205269B4 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113167275A (en) * | 2018-12-04 | 2021-07-23 | 株式会社日立产机系统 | Screw compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP4112940A4 (en) | 2020-02-27 | 2023-04-26 | Mitsubishi Electric Corporation | Screw compressor and freezer |
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| CN101334036A (en) * | 2007-06-29 | 2008-12-31 | 上海汉钟精机股份有限公司 | Semi-closed screw type refrigerating compressor air guide sleeve |
| JP2013167211A (en) * | 2012-02-16 | 2013-08-29 | Hitachi Appliances Inc | Screw compressor |
| CN104074768A (en) * | 2013-03-29 | 2014-10-01 | 珠海格力电器股份有限公司 | Screw rod compressor |
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| JPS5832990B2 (en) | 1977-10-28 | 1983-07-16 | 株式会社ナカ技術研究所 | evacuation device |
| JPS5832990A (en) * | 1981-08-24 | 1983-02-26 | Hitachi Ltd | Screw compressor |
| JPH0663506B2 (en) | 1987-02-28 | 1994-08-22 | 株式会社日立製作所 | Hermetic scroll compressor |
| JPH01237389A (en) | 1988-03-16 | 1989-09-21 | Hitachi Ltd | Screw compressor |
| JPH08322169A (en) * | 1995-05-23 | 1996-12-03 | Toshiba Corp | Motor |
| JP2015001220A (en) * | 2013-06-18 | 2015-01-05 | ダイキン工業株式会社 | Screw compressor |
| JP2016144356A (en) * | 2015-02-04 | 2016-08-08 | トヨタ自動車株式会社 | Rotor for rotary electric machine |
| JP6445948B2 (en) * | 2015-09-10 | 2018-12-26 | 日立ジョンソンコントロールズ空調株式会社 | Screw compressor |
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2017
- 2017-04-10 JP JP2017077538A patent/JP7075721B2/en active Active
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2018
- 2018-04-02 CN CN201810284820.6A patent/CN108691770B/en active Active
- 2018-04-09 DE DE102018205269.7A patent/DE102018205269B4/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101334036A (en) * | 2007-06-29 | 2008-12-31 | 上海汉钟精机股份有限公司 | Semi-closed screw type refrigerating compressor air guide sleeve |
| JP2013167211A (en) * | 2012-02-16 | 2013-08-29 | Hitachi Appliances Inc | Screw compressor |
| CN104074768A (en) * | 2013-03-29 | 2014-10-01 | 珠海格力电器股份有限公司 | Screw rod compressor |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113167275A (en) * | 2018-12-04 | 2021-07-23 | 株式会社日立产机系统 | Screw compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108691770B (en) | 2019-12-10 |
| DE102018205269B4 (en) | 2023-12-14 |
| JP2018178815A (en) | 2018-11-15 |
| JP7075721B2 (en) | 2022-05-26 |
| DE102018205269A1 (en) | 2018-10-11 |
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